|Publication number||US6834218 B2|
|Application number||US 10/378,225|
|Publication date||Dec 21, 2004|
|Filing date||Mar 3, 2003|
|Priority date||Nov 5, 2001|
|Also published as||US7027903, US7130735, US20030163231, US20040199314, US20050177296|
|Publication number||10378225, 378225, US 6834218 B2, US 6834218B2, US-B2-6834218, US6834218 B2, US6834218B2|
|Inventors||Joseph Carr Meyers, Todd Allen Brown|
|Original Assignee||Ford Global Technologies, Llc|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (220), Non-Patent Citations (7), Referenced by (48), Classifications (47), Legal Events (6)|
|External Links: USPTO, USPTO Assignment, Espacenet|
The present application is a continuation of U.S. patent application 09/682,974 entitled “ROLL OVER STABILITY CONTROL FOR AN AUTOMOTIVE VEHICLE” filed on Nov. 5, 2001, now Pat. No. 6,529,803.
The present invention relates generally to a dynamic behavior control apparatus for an automotive vehicle, and more specifically, to a method and apparatus for controlling the roll characteristics of the vehicle by changing a brake pressure distribution changing a steering angle or combination of both.
Dynamic control systems for automotive vehicles have recently begun to be offered on various products. Dynamic control systems typically control the yaw of the vehicle by controlling the braking effort at the various wheels of the vehicle. Yaw control systems typically compare the desired direction of the vehicle based upon the steering wheel angle and the direction of travel. By regulating the amount of braking at each corner of the vehicle, the desired direction of travel may be maintained. Typically, the dynamic control systems do not address roll of the vehicle. For high profile vehicles in particular, it would be desirable to control the roll over characteristic of the vehicle to maintain the vehicle position with respect to the road. That is, it is desirable to maintain contact of each of the four tires of the vehicle on the road.
Vehicle rollover and tilt control (or body roll) are distinguishable dynamic characteristics. Tilt control maintains the vehicle body on a plane or nearly on a plane parallel to the road surface. Roll over control is maintaining the vehicle wheels on the road surface. One system of tilt control is described in U.S. Pat. No. 5,869,943. The '943 patent uses the combination of yaw control and tilt control to maintain the vehicle body horizontal while turning. The system is used in conjunction with the front outside wheels only. To control tilt, a brake force is applied to the front out-side wheels of a turn. One problem with the application of a brake force to only the front wheels is that the cornering ability of the vehicle may be reduced. Another disadvantage of the system is that the yaw control system is used to trigger the tilt control system. During certain vehicle maneuvers, the vehicle may not be in a turning or yawing condition but may be in a rollover condition. Such a system does not address preventing rollover in a vehicle.
It would therefore be desirable to provide a roll stability system that detects a potential rollover condition as well as to provide a system not dependent upon a yaw condition.
It is therefore an object of the invention to provide a roll control system for use in a vehicle that is not dependent upon the turning condition of the vehicle.
In one aspect of the invention, stability control system for an automotive vehicle includes a plurality of sensors sensing the dynamic conditions of the vehicle and a controller that controls a distributed brake pressure to reduce a tire moment so the net moment of the vehicle is counter to the roll direction. The sensors include a speed sensor, a lateral acceleration sensor, a roll rate sensor, and a yaw rate sensor. A controller is coupled to the speed sensor, the lateral acceleration sensor, the roll rate sensor, the yaw rate sensor. The controller determines a roll angle estimate in response to lateral acceleration, roll rate, vehicle speed, and yaw rate. The controller determines a brake pressure distribution in response to the relative roll angle estimate. The controller may also use longitudinal acceleration and pitch rate to determine the roll angle estimate.
In a further aspect of the invention, a method of controlling roll stability of the vehicle comprises determining a roll angle estimate in response to lateral acceleration, roll rate, vehicle speed, and yaw rate, and determining a brake pressure distribution in response to the relative roll angle estimate.
One advantage of the invention is that the turning radius of the vehicle is not affected by the roll stability control.
Other objects and features of the present invention will become apparent when viewed in light of the detailed description of the preferred embodiment when taken in conjunction with the attached drawings and appended claims.
FIG. 1 is a diagrammatic rear view of a vehicle with force vectors not having a roll stability system according to the present invention.
FIG. 2 is a diagrammatic rear view of a vehicle with force vectors having a roll stability system according to the present invention.
FIG. 3 is a block diagram of a roll stability system according to the present invention.
FIG. 4 is a flow chart of a yaw rate determination according to the present invention.
FIG. 5 is a flow chart of roll rate determination according to the present invention.
FIG. 6 is a flow chart of a lateral acceleration determination according to the present invention.
FIG. 7 is a flow chart of chassis roll angle estimation and compensation.
FIG. 8 is a flow chart of a relative roll calculation.
FIG. 9 is a flow chart of system feedback for the right side of the vehicle resulting in brake distribution force.
FIG. 10 is a flow chart of system feedback for the left side of the vehicle.
FIG. 11 is a flow chart of another embodiment similar to that of FIGS. 9 and 10 resulting in change in steering position.
Referring to FIG. 1, an automotive vehicle 10 without a rollover stability system of the present invention is illustrated with the various forces and moments thereon during a rollover condition. Vehicle 10 has right and left tires 12 and 13 respectively. The vehicle may also have a number of different types of steering configurations including having each of the front and rear wheels configured with an independently controllable actuator, the front and rear wheels having a conventional type system in which both of the front wheels are controlled together and both of the rear wheels are controlled together, a system having conventional front steering and independently controllable rear steering for each of the wheels or vice versa. Variation of a control system for each will be described below. Generally, the vehicle has a weight represented as M*g at the center of gravity of the vehicle. A gravity moment 14 acts about the center of gravity (CG) in a counter-clockwise direction. A tire moment 16 acts in a clockwise direction about the center of gravity. Thus, the net moment 18 acting upon the vehicle is in a clockwise direction and thus increases the roll angle 20 of the vehicle. The lateral force 22 at the tire 12 on the ground (tire vector) is a significant force to the left of the diagram capable of overturning the vehicle if uncorrected.
Referring now to FIG. 2, a roll stability control system 24 is included within vehicle 10, which is in a roll condition. The forces illustrated in FIG. 2 are given the same reference numerals as the forces and moments in FIG. 1. In FIG. 2, however, roll stability controller 24 reduces the tire moment 16 to provide a net moment 18 in a counter-clockwise direction. Thus, the tire vector or lateral force 22 at tire 12 is reduced as well. This tendency allows the vehicle to tend toward the horizontal and thus reduce angle 20.
Referring now to FIG. 3, roll stability control system 24 has a controller 26 used for receiving information from a number of sensors which may include a yaw rate sensor 28, a speed sensor 30, a lateral acceleration sensor 32, a roll rate sensor 34, a steering angle sensor 35, a longitudinal acceleration sensor 36, a pitch rate sensor 37 steer and a steering angle position sensor 39. Lateral acceleration, roll orientation and speed may be obtained using a global positioning system (Global Positioning System). Based upon inputs from the sensors, controller 26 controls a tire force vector by steering control 38 as will be further described below or changing the steering angle of front right actuator 40 a, front left actuator 40 b, rear left actuator 40 c and/or rear right actuator 40 d. As described above, two or more of the actuators may be simultaneously controlled. For example, in a rack-and-pinion system, the two wheels coupled thereto are simultaneously controlled. Brake control 42 controls the front right brake 44 a, the front left brake 44 b, the rear left brake 44 c, and the right rear brake 446 d. Based on the inputs from sensors 28 through 39, controller 26 determines a roll condition and controls the brake pressure of the brakes on the appropriate side of the vehicle and/or steering angle. The braking pressure and/or steering angle is balanced on the side of the vehicle to be controlled between the front and rear brakes to minimize the induced yaw torque and induced path deviation. Depending on the desired sensitivity of the system and various other factors, not all the sensors 28-39 may be used in a commercial embodiment.
Roll rate sensor 34 and pitch rate sensor 37 may sense the roll condition of the vehicle based on sensing the height of one or more points on the vehicle relative to the road surface. Sensors that may be used to achieve this include a radar-based proximity sensor, a laser-based proximity sensor and a sonar-based proximity sensor.
Roll rate sensor 34 and pitch rate sensor 37 may also sense the roll condition based on sensing the linear or rotational relative displacement or displacement velocity of one or more of the suspension chasse components which may include a linear height or travel sensor, a rotary height or travel sensor, a wheel speed sensor used to look for a change in velocity, a steering wheel position sensor, a steering wheel velocity sensor and a driver heading command input from an electronic component that may include steer by wire using a hand wheel or joy stick.
The roll condition may also be sensed by sensing the force or torque associated with the loading condition of one or more suspension or chassis components including a pressure transducer in an act of suspension, a shock absorber sensor such as a load cell, a strain gauge, the steering system absolute or relative motor load, the steering system pressure of the hydraulic lines, a tire laterally force sensor or sensors, a longitudinal tire force sensor, a vertical tire force sensor or a tire sidewall torsion sensor.
The potential of a roll condition is associated with a zero normal load or a wheel lift condition on one or more of the wheels. A zero normal load, and thus a roll condition may be determined by sensing the force or torque associated with the loading condition of one or more suspension or chassis components including a pressure transducer in a suspension actuator. Similarly, a load cell or a strain gauge may be mounted to measure the force in a suspension component. The zero normal load condition may be used alone or in combination with other displacement or inertial measurements to accurately monitor the vehicle roll condition.
The power steering system actuation can be monitored to infer the normal load on the steered wheels. The steering load can be monitored by measuring one or more of the absolute or relative motor load, the steering system pressure of the hydraulic lines, tire lateral force sensor or sensors, a longitudinal tire force sensor(s), vertical tire force sensor(s) or tire sidewall torsion sensor(s) The steering system measurements used depend on the steering system technology and the sensors available on the vehicle.
The roll condition of the vehicle may also be established by one or more of the following translational or rotational positions, velocities or accelerations of the vehicle including a roll gyro, the roll rate sensor 34, the yaw rate sensor 28, the lateral acceleration sensor 32, a vertical acceleration sensor, a vehicle longitudinal acceleration sensor, lateral or vertical speed sensor including a wheel-based speed sensor, a radar-based speed sensor, a sonar-based speed sensor, a laser-based speed sensor or an optical-based speed sensor.
Speed sensor 30 may be one of a variety of speed sensors known to those skilled in the art. For example, a suitable speed sensor may include a sensor at every wheel that is averaged by controller 26. Preferably, the controller translates the wheel speeds into the speed of the vehicle. Yaw rate, steering angle, wheel speed and possibly a slip angle estimate at each wheel may be translated back to the speed of the vehicle at the center of gravity (V_CG). Various other algorithms are known to those skilled in the art. Speed may also be obtained from a transmission sensor. For example, if speed is determined while speeding up or braking around a corner, the lowest or highest wheel speed may be not used because of its error. Also, a transmission sensor may be used to determine vehicle speed.
Referring now to FIG. 4, the yaw rate sensor 28 generates a raw yaw rate signal (YR_Raw). A yaw rate compensated and filtered signal (YR_CompFlt) is determined. The velocity of the vehicle at center of gravity (V_CG), the yaw rate offset (YR_Offset) and the raw yaw rate signal from the yaw rate sensor (YR_Raw) are used in a yaw rate offset initialization block 45 to determine an initial yaw rate offset. Because this is an iterative process, the yaw rate offset from the previous calculation is used by yaw rate offset initialization block 45. If the vehicle is not moving as during startup, the yaw rate offset signal is that value which results in a compensated yaw rate of zero. This yaw rate offset signal helps provide an accurate reading. For example, if the vehicle is at rest, the yaw rate signal should be zero. However, if the vehicle is reading a yaw rate value then that yaw rate value is used as the yaw rate offset. The yaw rate offset signal along with the raw yaw rate signal is used in the anti-windup logic block 46. The anti-windup logic block 46 is used to cancel drift in the yaw rate signal. The yaw rate signal may have drift over time due to temperature or other environmental factors. The anti-windup logic block also helps compensate for when the vehicle is traveling constantly in a turn for a relatively long period. The anti-windup logic block 46 generates either a positive compensation OK signal (Pos Comp OK) or a negative compensation OK signal (Neg Comp OK). Positive and negative in this manner have been arbitrarily chosen to be the right and left direction with respect to the forward direction of the vehicle, respectively. The positive compensation OK signal, the negative compensation OK signal and the yaw rate offset signal are inputs to yaw rate offset compensation logic block 47.
The yaw rate offset compensation logic block 47 is used to take data over a long period of time. The data over time should have an average yaw of zero. This calculation may be done over a number of minutes. A yaw rate offset signal is generated by yaw rate offset compensation logic 47. A summing block 48 sums the raw yaw rate signal and the yaw rate offset signal to obtain a yaw rate compensated signal (YR_Comp).
A low pass filter 49 is used to filter the yaw rate compensated signal for noise. A suitable cutoff frequency for low pass filter 49 is 20 Hz.
Referring now to FIG. 5, a roll rate compensated and filtered signal (RR_CompFlt). The roll rate compensated and filtered signal is generated in a similar manner to that described above with respect to yaw rate. A roll rate offset initialization block 50 receives the velocity at center of gravity signal and a roll rate offset signal. The roll rate offset signal is generated from a previous iteration. Like the yaw rate, when the vehicle is at rest such as during startup, the roll rate offset signal is zero.
A roll rate offset compensation logic block 52 receives the initialized roll rate offset signal. The roll rate offset compensation logic generates a roll rate offset signal which is combined with the roll rate raw signal obtained from the roll rate sensor in a summing block 54. A roll rate compensated signal (RR_Comp) is generated. The roll rate compensated signal is filtered in low pass filter 56 to obtain the roll rate compensated and filtered signal that will be used in later calculations.
Referring now to FIG. 6, the raw lateral acceleration signal (Lat Acc Raw) is obtained from lateral acceleration sensor 32. The raw lateral acceleration signal is filtered by a low pass filter to obtain the filtered lateral acceleration signal (Lat Acc Flt). The filter, for example, may be a 20 Hz low pass filter.
Referring now to FIG. 7, a roll angle estimation signal (RollAngleEst) is determined by chassis roll estimation and compensation procedure 62. Block 64 is used to obtain a longitudinal vehicle speed estimation at the center of gravity of the vehicle. Various signals are used to determine the longitudinal vehicle speed at the center of gravity including the velocity of the vehicle at center of gravity determined in a previous loop, the compensated and filtered yaw rate signal determined in FIG. 4, the steering angle, the body slip angle, the front left wheel speed, the front right wheel speed, the rear left wheel speed, and the rear right wheel speed.
The new velocity of the center of gravity of the vehicle is an input to body roll angle initialization block 66. Other inputs to body roll angle initialization block 66 include roll angle estimate from the previous loop and a filtered lateral acceleration signal derived in FIG. 6. An updated roll angle estimate is obtained from body roll angle initialization. The updated roll angle estimate, the compensation and filtered roll rate determination from FIG. 5, and the time of the loop is used in body roll angle integration block 68. The updated roll angle estimate is equal to the loop time multiplied by the compensated and filtered roll rate which is added to the previous roll angle estimate obtained in block 66. The updated roll angle estimate is an input to roll angle estimate offset compensation block 70.
The velocity at the center of gravity of the vehicle is also an input to instantaneous roll angle reference block 72. Other inputs to instantaneous roll angle reference block 72 include the compensated and filtered yaw rate from FIG. 4 and the filtered lateral acceleration signal from FIG. 6. The following formula is used to determine a reference roll angle:
Where g is the gravitational constant 9.81 m/s2.
The reference roll angle from block 72 is also an input to roll angle estimate offset compensation. The updated roll angle estimation is given by the formula:
Where Tau is a time constant and may be a function of steering velocity, LatAcc and V-CG. A suitable time constant may, for example, be 30 seconds.
Referring now to FIG. 8, a relative roll angle estimation (RelativeRollAngleEst) and a road bank angle estimate signal is determined. The first step of the relative roll angle calculation involves the determination of road bank angle compensation time constant (Tau) block 72. The velocity at the center of gravity, the steering velocity and the filtered lateral acceleration signal from FIG. 6 are used as inputs. A compensated and filtered roll rate (RR_CompFlt) is used as an input to a differentiator 74 to determine the roll acceleration (Roll Acc). Differentiator 74 takes the difference between the compensated and filtered roll rate signal from the previous loop and the compensated and filtered roll rate from the current loop divided by the loop time to attain the roll acceleration. The roll acceleration signal is coupled to a low pass filter 76. The filtered roll acceleration signal (Roll Acc Flt), roll angle estimate, the filtered lateral acceleration signal and the loop time are coupled to chassis relative roll observer block 78. The chassis roll observer 78 determines the model roll angle estimation (Model Roll Angle Est). The model roll angle is a stable estimation of the roll dynamics of the vehicle which allows the estimates to converge to a stable condition over time.
From the model roll angle estimation from block 78, the initial relative roll angle estimation from block 72, a road bank angle initialization from a block 79 loop time and a roll angle estimate, road bank angle compensation block 80 determines a new road bank angle estimate. The formula for road bank angle is:
The roll angle estimate may be summed with the road bank angle estimate from block 80 in summer 82 to obtain a relative roll angle estimate. The road bank angle estimate may be used by other dynamic control systems.
Referring now to FIG. 9, the relative roll angle estimate from FIG. 8 and a relative roll deadband are summed in summer 84 to obtain an upper roll error. The upper roll error is amplified in KP_Roll Amplifier 86 and is coupled to summer 88. The roll rate compensated and filtered signal from FIG. 5 is coupled to KD_Roll Amplifier 90. The amplified roll rate signal is coupled to summer 88. The filtered roll acceleration signal from block 8 is coupled to KDD_Roll Amplifier 82. The amplified signal is also coupled to summer 88. The proportioned sum of the amplified signals is the right side braking force effort. From this, the right side brake force distribution calculation block 94 is used to determine the distribution of brake pressure between the front and rear wheels. The front right normal load estimate and the rear right normal load estimate are inputs to block 94. The front right roll control desired pressure and the right rear roll control desire pressure are outputs of block 94. The block 94 proportions the pressure between the front right and rear right signals to prevent roll. The front right, for example, is proportional according to the following formula:
The output of block 94 is used by the brake controller of FIG. 3 to apply brake pressure to the front right and rear right wheels. The brake controller factors in inputs such as the brake pressure currently applied to the vehicle through the application of pressure by the driver on the brake pedal. Other inputs include inputs from other dynamic control systems such as a yaw control system.
Referring now to FIG. 10, a similar calculation to that of FIG. 9 is performed for the left side of the vehicle. The relative roll angle estimate and relative roll deadband are inputs to summing block 96. However, the signs are changed to reflect that the left side of the vehicle is a negative side of the vehicle. Therefore, relative roll angle estimate and relative roll deadband are purely summed together 96 in summing block 96 to obtain the lower roll error. The lower roll error is passed through KP_Roll amplifier 98. The compensated and filtered roll rate is passed through KD_Roll amplifier 100 and the filtered roll acceleration signal is passed through KDD_Roll amplifier 102. The inverse of the signals from amplifiers 98, 100 and 102 are input and summed in summer 104 to obtain the left side braking effort.
A left side brake force distribution calculation block 106 receives the left side braking effort from summer 104. The front left normal load estimate and the rear left normal load estimate. In a similar manner to that above, the front left and rear left roll control brake pressures are determined. By properly applying the brakes to the vehicle, the tire moment is reduced and the net moment of the vehicle is counter to a roll direction to reduce the roll angle and maintain the vehicle in a horizontal plane.
Referring now to FIG. 11, a change in steering angle may be effectuated rather than or in combination with a change in brake force distribution. In either case, however, the tire force vector is changed. In FIG. 11, the same reference numerals as those in FIGS. 9 and 10 are used but are primed. Everything prior to blocks 88′ and 104′ is identical. Blocks 88′ and 104′ determine right side steering effort and left side steering effort, respectively.
The proportioned sum of the amplified signals is the right side steering tire correction. The rear (and front) steering actuator control signals are calculated from the tire corrections, the front and rear steer angles or the actuator positions, the vehicle side slip angle, the vehicle yaw rate and vehicle speed. Increased accuracy and robustness can be achieved by including tire normal load estimates and/or tire slip ratios. In the steering angle and effort correction block 94, the tire slip angles are calculated and used to determine the corrections to the rear (and front) steer angles that will reduce the tire lateral forces and reduce the vehicle roll angle. Block 94 also calculates the actuator control signals necessary to achieve the desired tire steering corrections.
The measured steering actuator positions are inputs to block 94. The change in the actuator direction and effort amounts and duration are outputs of block 94. The block 94 determines the appropriate direction and force amount to apply to the steering actuators to prevent roll.
The output of block 94 is used by the steering controller 38 of FIG. 3 to apply the desired steering to the front and/or rear wheels depending on the type of steering system. The steering controller factors in inputs such as the current steering position and the dynamics of the vehicle. Other inputs may include inputs from other dynamic control systems such as a yaw control system. In a production ready embodiment, the vehicle design characteristics will be factored into the desired control based on the sensor outputs.
The bottom portion of FIG. 9 is similar to the top, however, the signs are changed to reflect that the left side of the vehicle is a negative side of the vehicle. Therefore, relative roll angle estimate and relative roll deadband are purely summed together 96 in summing block 96 to obtain the lower roll error. The lower roll error is passed through KP_Roll amplifier 98. The compensated and filtered roll rate is passed through KD_Roll amplifier 100 and the filtered roll acceleration signal is passed through KDD_Roll amplifier 102. The inverse of the signals from amplifiers 98, 100 and 102 are input and summed in summer 104 to obtain the desired left actuator control.
By properly applying a desired steering control to the vehicle, the tire moment is reduced and the net moment of the vehicle is counter to a roll direction to reduce the roll angle and maintain the vehicle in a horizontal plane.
If both steering and brake distribution are used controller 26 will be used to apportion the amount of correction provided by steering and brake distribution. The amount of apportionment will depend on the roll rate and other variables for the particular vehicle. The amount of apportionment will thus be determined for each vehicle. For example, higher profile vehicles will be apportioned differently from a low profile vehicle.
In operation, various types of steering control may be performed depending on the vehicle characteristics and the steering system. For example, as described above a rack system may be controlled to provide a desired change in the rear steering angle temporarily to prevent rollover while leaving the front wheels unchanged. Of course, the direction of the front wheels could also be change when the rear direction is changed.
In a system having independently actuable front wheels, the relative steering angle between the front wheels may be changed in response to detected roll by steering control 38 without changing the position or controlling the position of the rear wheel. This may be done by independent control of the front wheels or simultaneous control of the front wheels.
In a system having independently actuable rear wheels, the relative steering angle between the front wheels may be changed in response to detected roll by steering control 38 without changing the position or controlling the position of the front wheels. This may be done by independent control of the rear wheels or simultaneous control of the rear wheels.
As described above the longitudinal acceleration sensor and a pitch rate sensor may be incorporated into the above tire force vector determination. These sensors may be used as a verification as well as an integral part of the calculations. For example, the pitch rate or the longitudinal acceleration or both can be used to construct a vehicle pitch angle estimate. This estimate along with its derivative can be used to improve the calculation of the vehicle roll angle. An example of how the rate of change of the vehicle roll angle using theses variables may be constructed is:
Where PitchRateCompFlt is a compensated and filtered pitch rate signal, GlobalRollAngleEst is an estimated global roll angle, VehiclePitchAngleEst is an estimated vehicle pitch angle estimate, and GlobalRR is a global roll rate signal. Of course, those skilled in the art may vary the above based upon various other factors depending on the particular system needs.
While particular embodiments of the invention have been shown and described, numerous variations and alternate embodiments will occur to those skilled in the art. Accordingly, it is intended that the invention be limited only in terms of the appended claims.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US2917126||Apr 4, 1957||Dec 15, 1959||Nolan Phillips||Driving control safety mechanism for tractors|
|US3604273||Nov 25, 1968||Sep 14, 1971||Aviat Electric Ltd||Angular rate sensor|
|US3608925||May 7, 1969||Sep 28, 1971||Murphy Peter H||Apparatus for offsetting centrifugal force affecting motor vehicles|
|US3899028||Aug 28, 1973||Aug 12, 1975||Systron Donner Corp||Angular position sensing and control system, apparatus and method|
|US3948567||Feb 12, 1975||Apr 6, 1976||The Bendix Corporation||Sway control means for a trailer|
|US3972543||Dec 6, 1974||Aug 3, 1976||The Bendix Corporation||Combination vehicle yaw stabilizer|
|US4023864||Sep 29, 1975||May 17, 1977||Lang Davis Industries, Inc.||Automatic stability control system with strain gauge sensors|
|US4480714||Jun 8, 1982||Nov 6, 1984||Toyo Umpanki Co., Ltd.||System for preventing carrier from turning sideways|
|US4592565||Oct 17, 1984||Jun 3, 1986||Leo Eagle||Apparatus for detecting an overturning moment in a moving vehicle, and jackknifing in a trailer-truck combination|
|US4597462||Jan 29, 1985||Jul 1, 1986||Honda Giken Kogyo Kabushiki Kaisha||Steering system for vehicles|
|US4650212||Mar 13, 1986||Mar 17, 1987||Mazda Motor Corporation||Vehicle suspension system|
|US4679808||Mar 7, 1986||Jul 14, 1987||Nissan Motor Co., Ltd.||Vehicle motion estimating system|
|US4690553||Jun 12, 1980||Sep 1, 1987||Omron Tateisi Electronics Co.||Road surface condition detection system|
|US4761022||Feb 24, 1987||Aug 2, 1988||Toyota Jidosha Kabushiki Kaisha||Suspension controller for improved turning|
|US4765649||Mar 16, 1987||Aug 23, 1988||Toyota Jidosha Kabushiki Kaisha||System for vehicle body roll control detecting and compensating for changes of loaded vehicle weight|
|US4767588||Apr 11, 1986||Aug 30, 1988||Nissan Motor Co., Ltd.||Vehicle control system for controlling side slip angle and yaw rate gain|
|US4778773||Jun 10, 1987||Oct 18, 1988||Nec Corporation||Method of manufacturing a thin film transistor|
|US4809183||Feb 25, 1987||Feb 28, 1989||Robert Bosch Gmbh||Speed control system for motor vehicles operating in a curved path|
|US4827416||Sep 12, 1986||May 2, 1989||Nissan Motor Company, Limited||Method and system for controlling automotive suspension system, particularly for controlling suspension characteristics in accordance with road surface conditions|
|US4872116||Mar 20, 1989||Oct 3, 1989||Nissan Motor Company, Limited||Vehicle motion estimating system of hybrid type|
|US4888696||Mar 31, 1988||Dec 19, 1989||Nissan Motor Company, Limited||Actively controlled automotive suspension system with acceleration and angular velocity dependent anti-pitching and/or anti-rolling feature|
|US4898431||Jun 15, 1988||Feb 6, 1990||Aisin Seiki Kabushiki Kaisha||Brake controlling system|
|US4930082||Jul 27, 1988||May 29, 1990||Mitsubishi Jidosha Kogyo Kabushiki Kaisha||Control apparatus for a vehicular suspension system|
|US4951198||Oct 14, 1988||Aug 21, 1990||Mazda Motor Corporation||Friction detecting device for vehicles|
|US4960292||Oct 11, 1989||Oct 2, 1990||Jaguar Cars Limited||Air bag restraint systems|
|US4964679||Feb 23, 1989||Oct 23, 1990||Lucas Industries Public Limited Co.||Monitoring method and apparatus for a brake system of heavy-duty vehicles|
|US4967865||Feb 13, 1989||Nov 6, 1990||Daimler-Benz Ag||Supplementary steering system|
|US4976330||Dec 6, 1988||Dec 11, 1990||Fuji Jukogyo Kabushiki Kaisha||Vehicle traction control system for preventing vehicle turnover on curves and turns|
|US4998593||Mar 31, 1989||Mar 12, 1991||Aisin Seiki Kabushiki Kaisha||Steering and brake controlling system|
|US5033770||Sep 22, 1989||Jul 23, 1991||Fuji Jukogyo Kabushiki Kaisha||Controlling apparatus for active suspension system for automotive vehicle|
|US5058017||Nov 2, 1988||Oct 15, 1991||Hitachi, Ltd.||System for control of vehicle suspension|
|US5066041||Jan 18, 1991||Nov 19, 1991||Baverische Motoren Werke Ag||Control system for stabilizing the rolling of a vehicle|
|US5088040||Jan 17, 1990||Feb 11, 1992||Nissan Motor Company, Limited||Automotive control system providing anti-skid steering|
|US5089967||Aug 20, 1990||Feb 18, 1992||Nippondenso Co., Ltd.||Auxiliary steering system associated with anti-skid control system for use in motor vehicle|
|US5163319||Oct 12, 1988||Nov 17, 1992||Messerschmitt-Bolkow-Blohm Gmbh||Method and a device for recognizing the condition of a road|
|US5200896||Sep 6, 1990||Apr 6, 1993||Honda Giken Kogyo Kabushiki Kaisha||Method for estimating longitudinal acceleration or deceleration of a vehicle body|
|US5208749||Aug 7, 1990||May 4, 1993||Hitachi, Ltd.||Method for controlling active suspension system on the basis of rotational motion model|
|US5224765||Dec 4, 1991||Jul 6, 1993||Nissan Motor Co., Ltd.||Control system for distributing braking forces applied to left and right wheels in automotive vehicles|
|US5228757||Jun 28, 1991||Jul 20, 1993||Nissan Motor Co., Ltd.||System for controlling behavior of vehicle during braking and during a steering maneuver|
|US5239868||Aug 24, 1992||Aug 31, 1993||Matsushita Electric Industrial Co., Ltd.||Angular rate detecting device|
|US5247466||Mar 25, 1991||Sep 21, 1993||Hitachi, Ltd.||Angular rate detection apparatus, acceleration detection apparatus and movement control apparatus, of moving body|
|US5261503||Dec 18, 1991||Nov 16, 1993||Aisin Seiki Kabushiki Kaisha||Adaptive steering control system|
|US5265020||Apr 18, 1991||Nov 23, 1993||Mazda Motor Corporation||Torque distribution control apparatus for four wheel drive|
|US5278761||Nov 12, 1992||Jan 11, 1994||Ford Motor Company||Method for vehicular wheel spin control that adapts to different road traction characteristics|
|US5282134||Aug 19, 1991||Jan 25, 1994||Automotive Systems Laboratory, Inc.||Slant transform/signal space crash discriminator|
|US5311431||Jul 1, 1992||May 10, 1994||Robert Bosch Gmbh||Method of obtaining the yawing velocity and/or transverse velocity of a vehicle|
|US5324102||Oct 19, 1992||Jun 28, 1994||Fag Kugelfischer Georg Schafer Kgaa||Method and apparatus for regulating the braking force of motorcycles|
|US5335176||Nov 30, 1992||Aug 2, 1994||Koyo Seiko Co., Ltd.||Safety system for vehicles|
|US5365439||Jul 5, 1991||Nov 15, 1994||Mitsubishi Jidosha Kogyo Kabushiki Kaisha||Method and apparatus for detecting friction coefficient of road surface, and method and system for four-wheel steering of vehicles using the detected friction coefficient of road surface|
|US5370199||Apr 6, 1993||Dec 6, 1994||Honda Giken Kogyo Kabushiki Kaisha||Vehicle traction control system|
|US5408411||Jan 17, 1992||Apr 18, 1995||Hitachi, Ltd.||System for predicting behavior of automotive vehicle and for controlling vehicular behavior based thereon|
|US5446658||Jun 22, 1994||Aug 29, 1995||General Motors Corporation||Method and apparatus for estimating incline and bank angles of a road surface|
|US5510989||May 23, 1995||Apr 23, 1996||Robert Bosch Gmbh||System for influencing the travel dynamics of an automobile|
|US5548536||Oct 17, 1994||Aug 20, 1996||Daimler-Benz Ag||Method for determining quantities which characterize the driving behavior|
|US5549328||Jan 17, 1995||Aug 27, 1996||Gabriel Ride Control Products, Inc.||Roll control system|
|US5579245||Feb 4, 1994||Nov 26, 1996||Mitsubishi Jidosha Kogyo Kabushiki Kaisha||Vehicle slip angle measuring method and a device therefor|
|US5598335||Apr 6, 1995||Jan 28, 1997||Hyundai Motor Company||System and method for controlling a shift position when a vehicle travels along a steeply sloped road or a sharply curved road|
|US5602734||Sep 23, 1994||Feb 11, 1997||Advanced Safety Concepts, Inc.||Automobile air bag systems|
|US5610575||Aug 25, 1994||Mar 11, 1997||Automotive Systems Laboratory, Inc.||Method and system for detecting vehicle roll-over|
|US5627756||Jun 2, 1995||May 6, 1997||Toyota Jidosha Kabushiki Kaisha||Device for controlling turn behavior of vehicle|
|US5634698||Feb 21, 1995||Jun 3, 1997||Robert Bosch Gmbh||System for controlling brake pressure based on fuzzy logic using steering angle and yaw speed|
|US5640324||Jan 27, 1995||Jun 17, 1997||Toyota Jidosha Kabushiki Kaisha||Dynamic behavior control apparatus of automotive vehicle|
|US5648903||Jul 10, 1995||Jul 15, 1997||Ford Global Technologies, Inc.||Four wheel steering control utilizing front/rear tire longitudinal slip difference|
|US5671982||Jun 7, 1995||Sep 30, 1997||Itt Automotive Europe Gmbh||System for applying a yawing control moment by setting brake valve opening and closing times|
|US5676433||Oct 22, 1996||Oct 14, 1997||Toyota Jidosha Kabushiki Kaisha||Device for estimating side slide velocity of vehicle compatible with rolling and cant|
|US5694319||Nov 8, 1996||Dec 2, 1997||Daimler-Benz Ag||Process for the determining travel-situation-dependent steering angle|
|US5703776||Apr 5, 1995||Dec 30, 1997||Hyundai Motor Company, Ltd.||Method and device for measuring slope of driving road|
|US5707117||Jul 19, 1996||Jan 13, 1998||General Motors Corporation||Active brake control diagnostic|
|US5707120||Oct 16, 1996||Jan 13, 1998||Toyota Jidosha Kabushiki Kaisha||Stability control device of vehicle improved against hunting|
|US5720533||Oct 15, 1996||Feb 24, 1998||General Motors Corporation||Brake control system|
|US5723782||Nov 29, 1996||Mar 3, 1998||Bolles, Jr.; Robert C.||Method of land vehicle suspension evaluation and design through roll angle analysis|
|US5732377||Jun 7, 1995||Mar 24, 1998||Itt Automotive Europe Gmbh||Process for controlling driving stability with a yaw rate sensor equipped with two lateral acceleration meters|
|US5732378||Jun 7, 1995||Mar 24, 1998||Itt Automotive Europe Gmbh||Method for determining a wheel brake pressure|
|US5732379||Jun 7, 1995||Mar 24, 1998||Itt Automotive Europe Gmbh||Brake system for a motor vehicle with yaw moment control|
|US5736939||Dec 11, 1996||Apr 7, 1998||Caterpillar Inc.||Apparatus and method for determing a condition of a road|
|US5737224||Jun 7, 1995||Apr 7, 1998||Robert Bosch Gmbh||Apparatus and method for tripping a system for the protection of occupants of a vehicle|
|US5740041||Oct 19, 1995||Apr 14, 1998||Toyota Jidosha Kabushiki Kaisha||Vehicle occupant restraint system responsive to accelleration|
|US5742918||Apr 26, 1996||Apr 21, 1998||Ford Global Technologies, Inc.||Method and apparatus for dynamically compensating a lateral acceleration of a motor vehicle|
|US5742919||Apr 26, 1996||Apr 21, 1998||Ford Global Technologies, Inc.||Method and apparatus for dynamically determining a lateral velocity of a motor vehicle|
|US5762406||Nov 14, 1996||Jun 9, 1998||Aisin Seiki Kabushiki Kaisha||Vehicle motion control system involving priority oversteer and understeer restraining control|
|US5782543||Oct 3, 1996||Jul 21, 1998||Toyota Jidosha Kabushiki Kaisha||Stability control device of vehicle compatible with foot braking|
|US5787375||Apr 1, 1996||Jul 28, 1998||Ford Global Technologies, Inc.||Method for determining steering position of automotive steering mechanism|
|US5801647||Sep 6, 1996||Sep 1, 1998||Vaisala Oy||Method and apparatus for measuring road surface conditions|
|US5809434||Apr 26, 1996||Sep 15, 1998||Ford Global Technologies, Inc.||Method and apparatus for dynamically determically determining an operating state of a motor vehicle|
|US5816670||Dec 4, 1996||Oct 6, 1998||Toyota Jidosha Kabushiki Kaisha||Vehicle brake control device|
|US5825284||Dec 10, 1996||Oct 20, 1998||Rollover Operations, Llc||System and method for the detection of vehicle rollover conditions|
|US5857535||Jan 29, 1997||Jan 12, 1999||Verward Pty. Limited||Seat for self-propelled narrow-track vehicle|
|US5869943||Oct 21, 1997||Feb 9, 1999||Aisin Seiki Kabushiki Kaisha||Vehicle motion control system|
|US5878357||Sep 3, 1996||Mar 2, 1999||Ford Global Technologies, Inc.||Method and apparatus for vehicle yaw rate estimation|
|US5893896||May 30, 1997||Apr 13, 1999||Unisia Jecs Corporation||Apparatus and method for stability controlling vehicular attitude using vehicular braking system|
|US5925083||Dec 8, 1997||Jul 20, 1999||Deutsche Forchungsanstalt Fur Luft Und Raumfahrt E.V.||Method of correcting steering of a road driven vehicle|
|US5931546||Oct 24, 1997||Aug 3, 1999||Aisin Seiki Kabushiki Kaisha||Vehicle motion control system|
|US5944137||Aug 28, 1997||Aug 31, 1999||Daimler-Benz Ag||Vehicle steering system|
|US5944392||Mar 27, 1996||Aug 31, 1999||Mazda Motor Corporation||Road surface condition determining system|
|US5946644||Mar 30, 1998||Aug 31, 1999||Chrysler Corporation||Steering center indicator device|
|US5964819||Jun 24, 1996||Oct 12, 1999||Nissan Motor Co., Ltd.||Vehicle yawing behavior control apparatus|
|US5971503||Feb 3, 1998||Oct 26, 1999||Ford Global Technologies, Inc.||Hydraulic control unit with ambient temperature compensation during fluid pressure delivery|
|US6002974||Feb 6, 1998||Dec 14, 1999||Delco Electronics Corporation||Vehicle rollover sensing using extended kalman filter|
|US6002975||Feb 6, 1998||Dec 14, 1999||Delco Electronics Corporation||Vehicle rollover sensing|
|US6026926||Jul 14, 1998||Feb 22, 2000||Honda Giken Kogyo Kabushiki Kaisha||Electric power steering apparatus|
|US6038495||Feb 6, 1998||Mar 14, 2000||Delco Electronics Corporation||Vehicle rollover sensing using short-term integration|
|US6040916||Aug 20, 1998||Mar 21, 2000||Daimlerchrysler Ag||Process and apparatus for determining the condition of a road surface|
|US6050360||Jun 24, 1998||Apr 18, 2000||General Motors Corporation||Apparatus and method for producing a desired return torque in a vehicle power steering system having a rotational steering position sensor|
|US6055472||Oct 17, 1996||Apr 25, 2000||Robert Bosch Gmbh||Arrangement for detecting motor-vehicle roll-overs|
|US6062336||Nov 13, 1998||May 16, 2000||General Motors Corporation||Adaptive variable effort power steering system|
|US6065558||Jun 30, 1998||May 23, 2000||Dynamotive, L.L.C.||Anti-rollover brake system|
|US6073065||Sep 4, 1998||Jun 6, 2000||Ford Global Technologies, Inc.||Method for detecting a bank angle experienced by a moving vehicle|
|US6079513||Feb 12, 1998||Jun 27, 2000||Koyo Seiko Co., Ltd||Steering apparatus for vehicle|
|US6081761||Apr 3, 1998||Jun 27, 2000||Mitsubishi Jidosha Kogyo Kabushiki Kaisha||Automatic deceleration control method and apparatus for a vehicle|
|US6085860||Mar 20, 1998||Jul 11, 2000||Robert Bosch Gmbh||Method and apparatus for operating a steering system for a motor vehicle|
|US6086168||Aug 15, 1997||Jul 11, 2000||Daimlerchrysler Ag||Method for operating a motor vehicle with driving-stabilizing brake interventions|
|US6089344||Jun 1, 1998||Jul 18, 2000||Ford Global Technologies, Inc.||Method and apparatus for determining the center position of a steering system|
|US6104284||Jun 14, 1999||Aug 15, 2000||Toyota Jidosha Kabushiki Kaisha||Roll over determining method|
|US6122568||Dec 22, 1998||Sep 19, 2000||Ford Global Technologies, Inc.||Method and apparatus for determining the dynamic stability of an automotive vehicle|
|US6122584||Feb 22, 1999||Sep 19, 2000||General Motors Corporation||Brake system control|
|US6129172||Jul 15, 1998||Oct 10, 2000||Koyo Seiko Co., Ltd.||Electric power steering apparatus|
|US6141604||Oct 10, 1996||Oct 31, 2000||Robert Bosch Gmbh||Method and arrangement for detecting a vehicle roll-over|
|US6141605||Jun 25, 1999||Oct 31, 2000||Ford Global Technologies, Inc.||Determining the direction of travel of an automotive vehicle from yaw rate and relative steering wheel angle|
|US6144904||Dec 22, 1998||Nov 7, 2000||Ford Global Technologies, Inc.||Instant detection / diagnosis of abrupt bias fault in signals of vehicle motion sensors|
|US6149251||Apr 9, 1997||Nov 21, 2000||Robert Bosch Gmbh||Process and device for controlling a braking force of at least one wheel of a vehicle|
|US6161905||Nov 19, 1998||Dec 19, 2000||General Motors Corporation||Active brake control including estimation of yaw rate and slip angle|
|US6169939||Sep 8, 1998||Jan 2, 2001||Ford Global Technologies, Inc.||Method of generating a vehicle lateral acceleration signal for use in an active tilt control system|
|US6176555||Nov 19, 1996||Jan 23, 2001||Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh||Method and device for controlling handling dynamics of motor vehicles|
|US6178375||Sep 15, 1998||Jan 23, 2001||Robert Bosch Gmbh||Method and device for determining the inertial position of a vehicle|
|US6179310||Dec 11, 1997||Jan 30, 2001||Rover Group Limited||Vehicle roll stabilizing system|
|US6179394||Nov 9, 1998||Jan 30, 2001||General Motors Corporation||Active brake balance control method|
|US6184637||Sep 30, 1999||Feb 6, 2001||Honda Giken Kogyo Kabushiki Kaisha||Electric power steering apparatus|
|US6185485||Dec 22, 1998||Feb 6, 2001||Ford Global Technologies, Inc||Relative vehicle platform having synchronized adaptive offset calibration for lateral accelerometer and steering angle sensor|
|US6186267||Mar 20, 1998||Feb 13, 2001||Robert Bosch Gmbh||Method and apparatus for operating a steering system for a motor vehicle|
|US6192305||May 18, 1998||Feb 20, 2001||Delco Electronics Corporation||Vehicle rollover sensing using yaw rate estimation|
|US6195606||Dec 7, 1998||Feb 27, 2001||General Motors Corporation||Vehicle active brake control with bank angle compensation|
|US6198988||Aug 10, 1998||Mar 6, 2001||Ford Global Technologies, Inc.||Method for detecting an erroneous direction of travel signal|
|US6202009||Dec 22, 1998||Mar 13, 2001||Ford Global Technologies, Inc.||Method for detecting fault of vehicle motion sensors|
|US6202020||Aug 20, 1999||Mar 13, 2001||Meritor Heavy Vehicle Systems, Llc||Method and system for determining condition of road|
|US6206383||May 26, 1999||Mar 27, 2001||Rover Group Limited||Hydraulic control systems|
|US6219604||Dec 28, 1999||Apr 17, 2001||Robert Bosch Gmbh||Steer-by-wire steering system for motorized vehicles|
|US6223114||Mar 22, 1999||Apr 24, 2001||Daimlerchrysler Ag||Process for controlling driving dynamics of a street vehicle|
|US6226579||Mar 20, 1998||May 1, 2001||Robert Bosch Gmbh||Method and apparatus for operating a steering system for a motor vehicle|
|US6233510||Oct 15, 1999||May 15, 2001||Meritor Heavy Vehicle Technology, Llc||Method and system for predicting road profile|
|US6263261||Dec 21, 1999||Jul 17, 2001||Ford Global Technologies, Inc.||Roll over stability control for an automotive vehicle|
|US6266596||Jun 13, 2000||Jul 24, 2001||Caterpillar Inc.||Method and apparatus for controlling a mobile machine during start-up|
|US6272420||Jul 29, 1998||Aug 7, 2001||Robert Bosch Gmbh||Method and device for detecting motor vehicle tilt|
|US6278930||Apr 25, 2000||Aug 21, 2001||Toyota Jidosha Kabushiki Kaisha||Device for controlling spin/driftout of vehicle compatibly with roll control|
|US6282471||Nov 17, 2000||Aug 28, 2001||Land Rover Group Limited||Vehicle roll control|
|US6282472||Mar 30, 1999||Aug 28, 2001||Trw Lucasvarity Electric Steering Ltd.||Electric power steering system with boost curve having portions defined by polynomial equations|
|US6282474||Jun 4, 2000||Aug 28, 2001||Ford Global Technologies, Inc.||Method and apparatus for detecting rollover of an automotive vehicle|
|US6292734||May 26, 2000||Sep 18, 2001||Toyota Jidosha Kabushiki Kaisha||Vehicle-behavior control apparatus and method|
|US6292759||Nov 19, 1998||Sep 18, 2001||Delphi Technologies, Inc.||Vehicle attitude angle estimation using sensed signal blending|
|US6311111||Jul 1, 1998||Oct 30, 2001||Robert Bosch Gmbh||Method and device for detecting motor vehicle tilt|
|US6314329||Nov 6, 1998||Nov 6, 2001||Visteon Global Technologies, Inc.||Compensation algorithm for initializing yaw rate sensor's zero point offset|
|US6315373||Mar 8, 2000||Nov 13, 2001||Toyota Jidosha Kabushiki Kaisha||Roll control device of vehicle manageable of sudden failure of rolling condition detection means|
|US6321141||Jun 30, 1998||Nov 20, 2001||Robert Bosch Gmbh||Method and device for detecting motor vehicle tilt|
|US6324446||Dec 21, 1999||Nov 27, 2001||Ford Global Technologies, Inc.||Roll over stability control for an automotive vehicle|
|US6324458||Aug 9, 2000||Nov 27, 2001||Toyota Jidosha Kabushiki Kaisha||Device for controlling vehicle turn behavior with discrimination of drive direction|
|US6330522||Sep 16, 1999||Dec 11, 2001||Kabushiki Kaisha Tokai Rika Denki Seisakusho||Rotational angle detector and method|
|US6332104||Dec 21, 1999||Dec 18, 2001||Ford Global Technologies, Inc.||Roll over detection for an automotive vehicle|
|US6338012||Jan 16, 2001||Jan 8, 2002||Ford Global Technologies, Inc.||Roll over stability control for an automotive vehicle|
|US6349247||Nov 24, 1998||Feb 19, 2002||Robert Bosch Gmbh||Method and device for stabilizing a motor vehicle in order to prevent it from rolling over|
|US6351694||Jan 16, 2001||Feb 26, 2002||Ford Global Technologies, Inc.||Method for robust estimation of road bank angle|
|US6352318||May 18, 2000||Mar 5, 2002||Toyota Jidosha Kabushiki Kaisha||Wheel control state display apparatus|
|US6356188||Sep 25, 2000||Mar 12, 2002||Ford Global Technologies, Inc.||Wheel lift identification for an automotive vehicle|
|US6370938||Nov 13, 1998||Apr 16, 2002||Robert Bosch Gmbh||Method and device for determining a quantity describing the height of the center of gravity of a vehicle|
|US6394240||Jan 20, 1999||May 28, 2002||Rover Group Limited||Vehicle roll damping|
|US6397127||Sep 25, 2000||May 28, 2002||Ford Global Technologies, Inc.||Steering actuated wheel lift identification for an automotive vehicle|
|US6419240||Sep 20, 1999||Jul 16, 2002||Land Rover||Vehicle roll control|
|US6428118||Sep 29, 1999||Aug 6, 2002||Robert Bosch Gmbh||Arrangement and methods for avoiding rollovers when braking or accelerating motor vehicles|
|US6438464||Jul 16, 1999||Aug 20, 2002||Continental Teves Ag & Co., Ohg||Method and device for detecting the overturning hazard of a motor vehicle|
|US6477480||Nov 15, 2000||Nov 5, 2002||Ford Global Technologies, Inc.||Method and apparatus for determining lateral velocity of a vehicle|
|US6496758||Nov 5, 2001||Dec 17, 2002||Ford Global Technologies, Inc.||Rollover stability control for an automotive vehicle using front wheel actuators|
|US6496763||Jan 8, 2001||Dec 17, 2002||Bayerische Motoren Werke Aktiengesellschaft||System for detecting vehicle rollovers|
|US6498976||Nov 1, 2000||Dec 24, 2002||Freightliner Llc||Vehicle operator advisor system and method|
|US6547022||Jun 22, 2001||Apr 15, 2003||Toyota Jidosha Kabushiki Kaisha||Vehicle traction control apparatus and method of traction control|
|US6554293||Nov 25, 1998||Apr 29, 2003||Continental Teves Ag & Co., Ohg||Method for improving tilt stability in a motor vehicle|
|US6556908||Mar 4, 2002||Apr 29, 2003||Ford Global Technologies, Inc.||Attitude sensing system for an automotive vehicle relative to the road|
|US6559634||Sep 21, 2001||May 6, 2003||Toyota Jidosha Kabushiki Kaisha||Vehicle wheel rotation detecting system and method|
|US20020014799||Jul 19, 2001||Feb 7, 2002||Toyota Jidosha Kabushiki Kaisha||Vehicular brake control apparatus and vehicular brake control method|
|US20020040268||Sep 28, 2001||Apr 4, 2002||Toyota Jidosha Kabushiki Kaisha||Apparatus for detecting rotational state of wheel|
|US20020056582||Jan 4, 2002||May 16, 2002||Chubb Erik Christopher||Wheel lift identification for an automotive vehicle|
|US20020075139||Dec 13, 2001||Jun 20, 2002||Toyota Jidosha Kabushiki Kaisha||Vehicle control apparatus and vehicle control method|
|US20020096003||Jan 14, 2002||Jul 25, 2002||Toyota Jidosha Kabushiki Kaisha||Running condition control system for vehicle and method|
|US20020139599||Feb 21, 2001||Oct 3, 2002||Jianbo Lu||Rollover stability control for an automotive vehicle using rear wheel steering and brake control|
|USRE30550||Apr 18, 1979||Mar 24, 1981||Durrell U. Howard||Automatic trailer sway sensing and brake applying system|
|DE3616907A1||May 20, 1986||Nov 26, 1987||Hans Prof Dr Ing Marko||Device for controlling the speed of revolution of a motor vehicle about the vertical axis|
|DE3815938C2||May 10, 1988||Sep 19, 1996||Bayerische Motoren Werke Ag||Beschleunigungs-Sensor für Fahrzeuge|
|DE4227886A1||Aug 22, 1992||Feb 24, 1994||Sel Alcatel Ag||Inclinometer for vehicle with body - contains inertial system or fibre optical gyroscope|
|DE4321571C2||Jun 29, 1993||Feb 3, 2000||Honda Motor Co Ltd||Verfahren zur Steuerung der Radlängskraft eines Fahrzeugs|
|DE4335979A1||Oct 21, 1993||Apr 27, 1995||Telefunken Microelectron||Sicherheits-Management-System (SMS)|
|DE4342732A1||Dec 15, 1993||Jun 22, 1995||Anton Ellinghaus Maschinenfabr||Tilt sensor for tanker vehicle|
|DE19907633A1||Feb 23, 1999||Oct 14, 1999||Bosch Gmbh Robert||Vehicle stabilization procedure, especially for avoiding vehicle tipping over about axis oriented in longitudinal direction|
|EP0430813B1||Nov 30, 1990||Dec 29, 1993||Regie Nationale Des Usines Renault S.A.||Safety device for motor vehicles|
|EP0662601B1||Mar 30, 1993||Dec 30, 1998||OKADA, Kazuhiro||Multishaft angular velocity sensor|
|EP0758601B1||Jul 3, 1996||Nov 28, 2001||MAN Nutzfahrzeuge Aktiengesellschaft||Procedure for on board determination of dynamic safety margins of utility vehicles|
|FR2425342A1||Title not available|
|GB2257403A||Title not available|
|GB2342078B||Title not available|
|JP1101238A||Title not available|
|JP2171373A||Title not available|
|JP3042360B2||Title not available|
|JP3045452B2||Title not available|
|JP4008837B2||Title not available|
|JP5016699B2||Title not available|
|JP5254406B2||Title not available|
|JP6278586A||Title not available|
|JP6297985A||Title not available|
|JP6312612A||Title not available|
|JP8080825A||Title not available|
|JP9005352A||Title not available|
|JP10024819A||Title not available|
|JP10329682A||Title not available|
|JP11011272A||Title not available|
|JP11170992A||Title not available|
|JP11254992A||Title not available|
|JP11255093A||Title not available|
|JP11304662A||Title not available|
|JP11304663A||Title not available|
|JP62055211B||Title not available|
|JP63116918U||Title not available|
|JP63151539U||Title not available|
|JP63203456A||Title not available|
|SU816849A1||Title not available|
|1||A method for reducing on-road rollovers-anti-rollover braking, Thomas J. Wielenga, Dynamotive, LLC, International Congress and Exposition, Detroit, Michigan, Mar. 1-4, 1999.|
|2||A method for reducing on-road rollovers—anti-rollover braking, Thomas J. Wielenga, Dynamotive, LLC, International Congress and Exposition, Detroit, Michigan, Mar. 1-4, 1999.|
|3||Eger, R., Kiencke, U., "Modeling of rollover sequences", Control Engineering Practice 11 (2003) 209-216.|
|4||Eger, R., Majjad, R., Naser, N., "Rollover simulation based on a nonlinear model", SAE 98020.|
|5||Nalecz, A.G., Bindemann, A.C., Brewer H.K., "Dynamic analysis of vehicle rollover", 12<th >International Conference on Experimental Safety Vehicles, Goteborg, Sweden, May 29-Jun. 1, 1989.|
|6||Nalecz, A.G., Bindemann, A.C., Brewer H.K., "Dynamic analysis of vehicle rollover", 12th International Conference on Experimental Safety Vehicles, Goteborg, Sweden, May 29-Jun. 1, 1989.|
|7||Niii, N., Nishijima, Y., Nakagawa, K., "rollover analysis method of a large-size bus", JSAE 9540020, 1995.|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US7063334 *||Apr 11, 2002||Jun 20, 2006||Howard Tak Su Lim||Vehicle stability system using active tilting mechanism|
|US7118184 *||Sep 29, 2004||Oct 10, 2006||Mitsubishi Fuso Truck And Bus Corporation||Roll-over suppressing control apparatus for a vehicle|
|US7162350 *||Jul 28, 2003||Jan 9, 2007||Advics Co., Ltd.||Vehicle motion control device|
|US7222007 *||Jan 7, 2004||May 22, 2007||Ford Global Technologies, Llc||Attitude sensing system for an automotive vehicle relative to the road|
|US7463965||Sep 29, 2004||Dec 9, 2008||Mitsubishi Fuso Truck And Bus Corporation||Roll-over suppressing control apparatus for a vehicle|
|US7573375||May 2, 2007||Aug 11, 2009||Paccar Inc||Rollover prediction and warning method|
|US7660654||Dec 13, 2004||Feb 9, 2010||Ford Global Technologies, Llc||System for dynamically determining vehicle rear/trunk loading for use in a vehicle control system|
|US7668645||Oct 15, 2004||Feb 23, 2010||Ford Global Technologies||System and method for dynamically determining vehicle loading and vertical loading distance for use in a vehicle dynamic control system|
|US7715965||Oct 25, 2004||May 11, 2010||Ford Global Technologies||System and method for qualitatively determining vehicle loading conditions|
|US7877178||Jan 5, 2010||Jan 25, 2011||Ford Global Technologies||System and method for dynamically determining vehicle loading and vertical loading distance for use in a vehicle dynamic control system|
|US7877199||Jan 5, 2010||Jan 25, 2011||Ford Global Technologies||System and method for dynamically determining vehicle loading and vertical loading distance for use in a vehicle dynamic control system|
|US7877200||Jan 5, 2010||Jan 25, 2011||Ford Global Technologies|
|US7877201||Jan 5, 2010||Jan 25, 2011||Ford Global Technologies|
|US7899594||Mar 10, 2010||Mar 1, 2011||Ford Global Technologies||System and method for qualitatively determining vehicle loading conditions|
|US8005592||Sep 3, 2009||Aug 23, 2011||Ford Global Technologies||System for dynamically determining axle loadings of a moving vehicle using integrated sensing system and its application in vehicle dynamics controls|
|US8005596||Dec 18, 2009||Aug 23, 2011||Ford Global Technologies||System for dynamically determining vehicle rear/trunk loading for use in a vehicle control system|
|US8050857||Jan 5, 2010||Nov 1, 2011||Ford Global Technologies|
|US8121758||Nov 9, 2005||Feb 21, 2012||Ford Global Technologies||System for determining torque and tire forces using integrated sensing system|
|US8191975 *||Dec 15, 2005||Jun 5, 2012||Bendix Commercial Vehicle Systems Llc||Single channel roll stability system|
|US8219282||Dec 18, 2009||Jul 10, 2012||Ford Global Technologies||System for dynamically determining vehicle rear/trunk loading for use in a vehicle control system|
|US8311706||Aug 6, 2009||Nov 13, 2012||Ford Global Technologies||Integrated vehicle control system using dynamically determined vehicle conditions|
|US8346433||May 9, 2012||Jan 1, 2013||Ford Global Technologies||System for dynamically determining vehicle rear/trunk loading for use in a vehicle control system|
|US8346452||Aug 6, 2009||Jan 1, 2013||Ford Global Technologies||Integrated vehicle control system using dynamically determined vehicle conditions|
|US8352143||Aug 6, 2009||Jan 8, 2013||Ford Global Technologies||Integrated vehicle control system using dynamically determined vehicle conditions|
|US8359146||May 23, 2008||Jan 22, 2013||Bendix Commercial Vehicle Systems Llc||Single channel roll stability system|
|US8442720||Aug 6, 2009||May 14, 2013||Ford Global Technologies||Integrated vehicle control system using dynamically determined vehicle conditions|
|US8649936 *||Mar 31, 2008||Feb 11, 2014||Penny & Giles Controls Limited||Method and apparatus for determining a value of a zero point offset of a yaw rate sensor|
|US8768572 *||Mar 12, 2003||Jul 1, 2014||Robert Bosch Gmbh||Apparatus for detecting a rollover event|
|US8892325||Mar 30, 2011||Nov 18, 2014||Advics Co., Ltd.||Vehicle motion controller|
|US9283825||Feb 25, 2015||Mar 15, 2016||Isam Mousa||System, method, and apparatus to prevent commercial vehicle rollover|
|US9718503 *||Jun 5, 2015||Aug 1, 2017||Gavin Ursich||Counter-torque rollover prevention architecture|
|US9719568||Aug 14, 2015||Aug 1, 2017||Honda Motor Co., Ltd.||All wheel drive hydraulic fluid pressure sensor compensation algorithm|
|US20020109310 *||Apr 11, 2002||Aug 15, 2002||Lim Howard Tak Su||Vehicle stability system using active tilting mechanism|
|US20050099065 *||Sep 29, 2004||May 12, 2005||Masaharu Harada||Roll-over suppressing control apparatus for a vehicle|
|US20050102084 *||Sep 30, 2004||May 12, 2005||Kunio Sakata||Roll-over suppressing control apparatus for a vehicle|
|US20050110345 *||Sep 29, 2004||May 26, 2005||Kunio Sakata||Roll-over suppressing control apparatus for a vehicle|
|US20050149240 *||Jan 7, 2004||Jul 7, 2005||Tseng Hongtei E.||Attitude sensing system for an automotive vehicle relative to the road|
|US20050251316 *||Jul 28, 2003||Nov 10, 2005||Toshihisa Kato||Motion control device of vehicle|
|US20060076741 *||Nov 28, 2005||Apr 13, 2006||Lim Howard T S||Vehicle stability system: using active tilting mechanism as a counter measure to natural tilt|
|US20060095182 *||Mar 12, 2003||May 4, 2006||Robert Lahmann||Apparatus for detecting a rollover event|
|US20070138865 *||Dec 15, 2005||Jun 21, 2007||Bendix Commercial Vehicle Systems, Llc||Single channel roll stability system|
|US20080272899 *||May 2, 2007||Nov 6, 2008||Paccar Inc||Rollover prediction and warning method|
|US20080288148 *||May 23, 2008||Nov 20, 2008||Bendix Commercial Vehicle Systems, Llc||Single Channel Roll Stability System|
|US20110035097 *||Mar 31, 2008||Feb 10, 2011||Jason Lewis||Method and apparatus for determining a value of a zero point offset of a yaw rate sensor|
|US20110093171 *||Nov 26, 2010||Apr 21, 2011||Fabio Saposnik||Machine loss-of-control detector and shutdown system|
|US20150353150 *||Jun 5, 2015||Dec 10, 2015||Gavin Ursich||Counter-torque rollover prevention architecture|
|WO2007054003A1 *||Sep 26, 2006||May 18, 2007||Beiqiang Xu||An electrical assist steering system with stabilization function and the method thereof|
|WO2007082041A1||Jan 12, 2007||Jul 19, 2007||T.K. Holdings Inc.||Control module|
|U.S. Classification||701/1, 701/38, 701/41|
|International Classification||B60T7/12, B60T8/40, G06F19/00, B60T8/44, B60T8/36, B62D6/00, B60T8/24, B60T8/172, B60T8/1755, B60W30/04|
|Cooperative Classification||B60G2400/104, B60G2400/0523, B60W2720/403, B60G2400/0521, B60W2030/043, B60W2720/18, B60G2800/012, B60W30/04, B60G2800/0124, B60T8/243, B60W10/184, B60G2800/922, B60G2800/215, B60T2210/22, B60G2400/64, B60T7/12, B60G2400/0511, B60G2800/016, B60W2550/14, B60T8/172, B60G2400/204, B60T2230/03, B60T2250/06, B60W2520/18, B62D6/00, B60W2550/402, B60G2800/702, B60T8/17554|
|European Classification||B60T8/24B2, B60W10/184, B60T7/12, B60T8/172, B62D6/00, B60T8/1755F|
|May 15, 2008||FPAY||Fee payment|
Year of fee payment: 4
|May 11, 2010||CC||Certificate of correction|
|May 25, 2012||FPAY||Fee payment|
Year of fee payment: 8
|Jul 29, 2016||REMI||Maintenance fee reminder mailed|
|Dec 21, 2016||LAPS||Lapse for failure to pay maintenance fees|
|Feb 7, 2017||FP||Expired due to failure to pay maintenance fee|
Effective date: 20161221